Heat pump

ABSTRACT

A heat pump having a closed cycle refrigeration system including a condenser, evaporator and compressor and a vaporized fluid power system for driving the compressor including a boiler and condenser. The condensers are arranged in such a manner that heat is transferred to the ambient when the apparatus is utilized to cool a conditioned zone and heat is transferred to the conditioned zone when the apparatus is utilized to heat a conditioned zone. The evaporator simultaneously removes heat from the conditioned zone during cooling thereof and removes heat from the ambient during heating of the conditioned zone. A fluid bypass system is provided to supply heat directly from the boiler to the condenser of the vaporized fluid power system during extreme, low ambient temperature conditions when the conditioned zone is being heated.

United States Patent Anderson 1 HEAT PUMP I James H. Anderson, I615Hilock Lane, York, Pa.

[22] Filed: Nov. 26, 1969 [21] App]. No.: 877,553

[76] Inventor:

Related US. Application Data [62] Division of Ser. No. 703,l56, Feb. 5,I968, Pat. No.

1 1 May 1, 1973 Primary Examiner-Charles Sultalo Attorney-Kemon, Palmerand Estabrook 5 7 ABSTRACT A heat pump having a closed cyclerefrigeration system including a condenser, evaporator and compressorand a vaporized fluid power system for driving the compressor includinga boiler and condenser. The condensers are arranged in such a mannerthat heat is transferred to the ambient when the apparatus is utilizedto cool a conditioned zone and heat is transferred to the conditionedzone when the apparatus is utilized to heat a conditioned zone. Theevaporator simultaneously removes heat from the conditioned zone duringcooling thereof and removes heat from the ambient during heating of theconditioned zone. A fluid bypass system is provided to supply heatdirectly from the boiler to the condenser of the vaporized fluid powersystem during extreme, low ambient temperature conditions when theconditioned zone is being heated.

5 Claims, 5 Drawing Figures Patented May 1, 1973 v 3,730,263

2 Sheets-Sheet 1 FIG.

INVENIOR JAMES H. ANDERSON l J v (I 1 V v 124 BY/jm ATTORNHJ PatentedMay .1, 1973 3,730,263

2 Sheets-Sheet 2 1 umui INVENTOR' JAMES H. ANDERSON HEAT PUMPCROSS-REFERENCE TO RELATED APPLICATION This is a division of applicationSer. No. 703,156 filed Feb. 5, I968, now U.S. Pat. No. 3,519,066.

BACKGROUND OF THE INVENTION I-Ieat pump apparatus are in wide use forheating and cooling buildings in the art. Prior art heat pumps generallyinclude a refrigeration system having a contional or supplementaryheating apparatus in conjunction therewith.

SUMMARY OF THE INVENTION This invention relates generally to devices fortransferring heat energy from a low temperature locality to a hightemperature locality and more specifically to a heat pump foraccomplishing such transfer by mechanical means involving thecompression and expansion of a fluid by mechanical refrigeration. Theinvention relates more particularly to such an apparatus as applied toheating or cooling a building by transferring heat from or to theambient air.

This invention provides a novel heat pump apparatus which avoids thedisadvantages of the prior art by furnishinga vaporized fluid powersystem including a condenser for powering a closed cycle refrigerationsystem whereby the condensers of the vaporized fluid power system and ofthe refrigeration system are utilized to selectively transfer heat tothe ambient or to the conditioned zone while the evaporator of therefrigeration system is utilized to extract heat from the-ambient or theconditioned zone. i

The invention also provides a novel evaporator-condenser structure whichmay be quickly manipulated to switch from the function of extraction ofheat from, to the transfer of heat to the conditioned zone.

The invention further provides novel means for bypassing the power unitof the vaporized fluid power system for circulating heat energy directlyto the condenser thereof to increase the heat output of the apparatusduring heating of the condition zone at low ambient temperatures.

In the preferred embodiment, the invention comprises a refrigerationsystem comprising a condenser, expansion means, evaporator andcompressor, the compressor being driven bya vaporized fluid power systemcomprising a rotary boiler, turbine and condenser. The condensers andevaporator are rotatably mounted in opposed relationship so that theevaporator may be mechanically moved from communication with theconditioned zone to communication with the ambient while the condensersare simultaneously moved F2 means to switch from transferof heat from,to transfer of heat to the conditioned zone. A bypass is provided tocommunicate fluid frornthe boiler of the vaporized fluid power system,around the turbine, directlyto the condenser thereof to increase theheat output of the vaporized fluid power system when required forheating the conditioned zone. I

These and other objects of the invention will become better understoodto those skilled in the art by reference to the following detaileddescription when viewed in light of the accompanying drawings whereinlike numerals throughout the figures thereof indicate like componentsand wherein:

FIG. 1 is a schematic view of a heat pump apparatus in accordance withthe invention;

FIG. 2 is a fragmentary plan view, in section, of theevaporator-condenser structure of the invention of FIG. 1 disposed inducting and configured to transfer 20 heat from the conditioned zone;

FIG. 3 is a view similar to FIG. 2 showing the evaporator with thecondenser structure of the invention disposed in such a manner totransfer heat to the conditioned zone;

5 FIG. 4 is a schematic view similar to FIG. 1 showing anotherembodiment of the invention; and

FIG. 5 is afragmentary plan view similar to FIG. 3 showing theevaporator-condenser structure of the embodiment of FIG. 4.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring now to FIG. 1 of thedrawings, the heat pump comprises a refrigeration apparatus including acondenser l0.communicating in series through a conduit 12 with anexpansion valve 14, evaporator 16 and i a compressor 18. Power for thecompressor 18 is derived from a vaporized fluid power system comprisinga turbine .20, connected to the compressor 18 at the portion thereofsupplying fluid to the turbine 20,

and serves to increase the pressure of the fluid circulating from thecondenser.26 to the boiler 30 in a manner well known in the art.

A bypass conduit 34, including a valve 36, communicates with the conduit24 on either side ofthe turbine 20 to provide a means to selectivelybypass theturbine. Air circulating means such as fans 38 and 40 aredisposed to induce airflow over the evaporator 16 and the condensers l0and-26 respectively.

matically as an axial flow rotary turbine-compressor, for example, thecompressor may take the form of a radial flow turbineand/or compressoror reciprocatory motor-compressor structure if so desired.

In the disclosed embodiment, it is contemplated that fluid in therefrigeration system will comprise one of V the suitable conventionalrefrigerants such, for example,-as ammonia or one of the fluorocarbons,while the fluid in the vaporized fluid power system will preferablycomprise a halogenated hydrocarbon suitable for the purpose such, I forexample, as Freon ll4 (dichlorotetrafluoroethane CClFgCClFz) orFreon-318 (octafluorocyclobutane C4F A vaporized fluid power systemparticularly suitable for this purpose is disclosed in U.S. Pat. No.3,315,466, issued Apr. 25, 1967. In the 1 event that such a fluid powersystem with a rotary turbine-compressor structure is utilized totransmit power between the vaporized fluid power system and therefrigeration system, segregation of the fluids and lubrication of theturbine-compressor may be accomplished with the bearing and seal systemdisclosed in U.S. Pat. No. 3,258,199, issued June 28, 1966.

In utilizing fluids such as the above-mentioned Freons as working fluidsin the vaporized fluid power system, cavitation problems are encounteredin transmitting the fluid from the condenser to the boiler. It iscontemplated that such problems, if encountered, can be overcome bysubcooling the fluid supplied to the injector 28 by means of a structuresuch as the subcooling column 16 disclosed in the'afore-mentioned U.S.Pat. No. 3,315,466.

Although the boiler 30 may be of any of the types common in the art, forthe purposes of compactness and eff ciency as well as for particularadaptability for use with fluorocarbons, it is preferred that a boilerstructure such as the rotary vapor generator disclosed in U.S. Pat. No.3,260,050, issued July 12, 1966, be utilized. If such a boiler is used,as disclosed in that patent, a major portion of the pumping worknecessary for circulating fluid through the vaporized fluid power systemcan be accomplished in the rotary boiler and the work required from theinjector can thereby be reduced or eliminated. For this reason, it ispossible that the injector 28 may be, in some cases, eliminated from thesystem by proper design.

Referring now to FIG.' 2 of the drawings, the evaporator 16 and thecondensers l and 26 are shown mounted in opposed substantially coplanarrelationship to one another on a rotatable member 42, disposed between aconditioned zone duct 44 and an ambient duct 46. The fans 38 and 40 aremounted in the ducts 44 and 46 respectively to circulate air as shown bythe arrows through the ducts. A movable panel 48 is disposed in anopening 50,.formed between the ducts 44 and 46 and is mounted forrotation on the rotatable member 42 in perpendicular relationship to thecondensers and 26 and the evaporator 16. A suitable elastic seal 52 isprovided between the panel 48 and the opening 50 to block communicationbetween the ducts 44 and 46 when the panel 48 is aligned therewith asillustrated.

A wall 56 segregates a conditioned zone, indicated generally at 58, froman ambient area, indicated generally at 60. The duct 44 penetrates thewall 56 through openings 62 and 64 to provide communication with theconditioned zone 58.

In operation, with the apparatus in the configuration illustrated inFIGS. 1 and 2 and the valve 36 (FIG. 1) closed, the conditioned zone 58is cooled by energization of the boiler 30 and the fans 38 and 40. Uponenergization of the boiler, as more particularly described inaforementioned U.S. Pat. No. 3,260,050, the vaporized fluid power systemoperates generally in accordance with that disclosed in aforementionedU.S. Pat. No. 3,315,466 with the substitution of the injector 28 for themain pump 20 and elimination of the recuperator 10 thereof. Heated, highpressure fluid is delivered through the conduit 24 to the turbine 20,thereby driving the compressor 18 through the shaft 22. Turbine exhaustfluid is directed through the conduit ,24 --to the condenser 26 wherebyheat is removed therefrom by passage of air therethrough by means of thefan 40 and the duct 46. Fluid is returned to the boiler 30 through theconduit 24 by means of the influence of the injector 28 deriving energyfor increasing the feed pressure to the boiler from a portion of highenergy fluid diverted thereto through the branch conduit 32 as describedabove.

Fluid, compressed in the compressor 18, is circulated through thecondenser 10 for removal of heat therefrom by air flow directedthereover by means of the fan 40 and the duct 46. The cooled highpressure fluid is then transmitted through the conduit 12 to theexpansion valve 14 for expansion and cooling thereof in a conventionalmanner. The expanded, cooled fluid is then transmitted through theevaporator 16 for transfer of heat thereto from conditioned zone airdirected thereover by means of the fan 38 and the duct 44 in a mannerwell known in the refrigeration art. The expanded, warmed refrigerationfluid is then returned to the compressor 18 for recycling thereof in aclosed cycle.

It should be noted at this point that the arrangement of the condensersl0 and 26 relative to the direction of air flow through the duct 46 isparticularly efficient since the Coefficient of Performance of a Carnotcycle is a function of the difference between the temperature of heat inand the temperature of heat rejected divided by the temperature of heatin as in the following relationship:

COP Carnot T1 2/ 1 while the Coefficient of Performance of arefrigerator is a function of the temperature of heat in, divided by thedifference between the temperature of heat rejected and the temperatureof heat in as in the following relationship: a

Reh-la.' a/ T2 T3 The overall Coefficient of Performance is then asfollows: I

Total 1 z/ i X s/ z a When the heat rejector or condenser structures areplaced in series, either the hot body of heat or the cold body of heatcan be rejected at the higher temperature. Presuming the following:

T, temperature of heat supplied I T temperature of heat rejected fromthe power condenser 26 T temperature of heat rejected from therefrigerator condenser 10 T temperature of heat supplied to refrigeratorthe overall Coefficient of Performance of the heat pump then is asfollows:

For example, by first placing the refrigerator condenser 10 upstream toreceive the coolest supply of air flow and assuming the following values(absolute):

For these parameters, the Coefficient of Performance is calculated asfollows: i t

COP=425/l010 505/80T2.59

By reversing the condensers and placingthe power condenser 26 upstreamof the refrigeration condenser with the above same assumptions, theparameters are:

The Coefficient of Performance then is as follows:

COP 425/1010 505/90 2.36 or an increase in Coefficient of Performance of0.23 by proper arrangement of the condensers, as illustrated.

Referring now to FIG. 3 of the drawings, the evaporator-condenser ofFIG. 2 is shown rotated, 180 to place the condensers l0 and 26 in theconditioned zone duct 44 and the evaporator 16 in the ambient duct 46.The panel 48 once more aligns with the ducts 44 and 46 to providesegregation of airflow therebetween.

Since fluid connection from the condensers 10 and 26 and the evaporator16 with the remainder of the system must be accomplished through sixconduits as described above, it is preferable, in order to avoidmultiple seal problems, to design the connections in such a manner thatcommunication is provided while allowing 180 rotation of the structure.Such communication may be accomplished by providing tubes formed ashelical springs twistable through 180 or communicating tubes ofsufficient length to permit a 180 twist without yielding the tubematerial. Ithas been found that such can be accomplished with steeltubes of the following characteristics, for example:

E,= 12 X 10 psi Straight length 58.9

S 20,000 psi d=0.625 inches It should be noted at this point, that sincethe condenser side of the structure would normally: have a higherresistance to airflow than the evaporator side, it is advisable to makeprovision for increasing the airflow through the condenser side of thestructure. This could be accomplished by providing a two-speedarrangement on the fans 38 and 40 so that the fans may be switched froma higher airflow when the condenser section is disposed in a particularduct to a lower airflow when the evaporator side is disposed therein.Another alternative would be to mount a supplementary fan on thecondenser structure to automatically compensate for the additional flowresistance therethrough.

With the apparatus structured in accordance with the configuration shownin FIG. 3, heat is supplied to the conditioned zone by means ofrejection from the condensers l0 and 26 disposed in the duct 44 whileheat is extracted from air circulated through the duct 46 by theevaporator 16. Heat supplied in this manner is suitable for moderatecold weather conditions and temperature may be controlled at a desiredlevel by regulating the amount of heat supplied to either or both of thecondensers 10 or 26. In moderate weather conditions, the compressorsupplies some heat to the condenser 10 while whatever additional heat isrequired may be extracted from the condenser 26.

In very cold weather conditions, the compressor 18 will normallynot'supply sufficient heat through the condenser 10 to enable the heatderived from the turbine through the condenser 26 to suitably'augmentthe heat output. Under these conditions, it is more efficient to removethe compressor from the line and direct heat generated by the boiler 30.directly to the condenser 26. This is accomplished by opening the valve36 and bypassing the turbine20 to channel the heated fluid for v theboiler 30 directly through the conduit 34 to the condenser 26, therebychanneling all of the heat from the boiler 30 to the airflow directly.

Referring now to FIG. 4 of the drawings, another embodiment inaccordance with the invention is illustrated. Since fluorocarbons suchas the above-mentioned Freons are equally suitable for use asrefrigants, the heat pump can utilize a single fluid system. This isaccomplished by joining the exhaust from the turbine and the dischargefrom the compressor and directing the flow to a common condenser. Insuch a system, illustrated in FIG. 4, components thereof correspondingto like of the preceding figures are indicated by like numerals of thenext higher order. In this figure the exhaust from the turbine 120 ismanifolded into a combined condenser 166 through the conduit 124 withthe exhaust or discharge from the compressor 118 fed through the conduit1l2. To condensate from the com denser 166 is divided subsequent tocondensation in the conduit 124, for return to the boiler 130, andtheconduit 112, for channeling through the expansion valve 114. Theoperation of the remainder of the system is identical to that describedfor the embodiment of FIG. 1.

In FIG. 5, the evaporator-condenser structure is shown disposed in theambient duct 146 and conditioned zone duct 144 and operates in amanneridentical to that described for the embodiment of FIGS. 2 and 3for switching from cooling, as illustrated, toheating of the conditionedzone.

In the single fluid system disclosed in FIGS. 4 and 5, it is possible tosubstitute an injection or jet type compression apparatus for the rotaryturbine-compressor illustrated. The principles of operation of such anapparatus are well known in the steam power plant art I and areillustrated by the injector 28 utilized in the embodiment of FIG. 1. Insuch a device, the high energy, high temperature fluid from the boiler130 would be injected through the conduit 124 into the low energy fluidin the conduit 112 after passage thereof through the evaporator 116,thereby raising the pressure and energy level of the fluid entering thecondenser'166. After cooling in the condenser 1166, the high energyfluid would then be divided as described above, a portion thereofreturning to the boiler 130 while the remainder thereof is expandedthrough the expansion valve 114 for reentry into the evaporator 116..

What has been set forth above is intended as exemplary of teachings inaccordance with the inventionto enable those skilled in the art in thepractice thereof. It should, therefore, be understood that, withinthescope of the appended claims, the invention may be practiced other thanas specifically described. What is new and therefore intended to beprotected by Letters Patent of the United States is:

1. In a heat pump system having parallel abutting airflow ductscommunicative with zones of differenttemperature, the improvementcomprising a heat exchange assembly including a compressor with drivingmeans therefore, and evaporator and at least one condenser, saidcondenser and evaporator of said heat assembly mounted on a rotatablemember in an opening between said ducts with said compressor and drivingmeans therefore arranged externally of said ducts, said condensermounted on said rotatable member on one side of the axis of rotation ofsaid member, said evaporator mounted in adjacent, substantially coplanarrelationship to said condenser on the other side of said axis ofrotation of said member, and a panel mounted substantially normal tosaid condenser and evaporator and intercepting said axis of rotation,said opening being substantially equal in area to the combined area ofsaid condenser and evaporator, said panel being coextensive andalignable in said opening with the common walls of said ducts to provideflow division there between.

2. A heat pump system in accordance with claim I wherein said heat pumpcomprises a vaporized fluid power system including a power condenser,and a closed cycle refrigeration system including a refrigerationcondenser.

3. A heat pump system in accordance with claim 2 wherein said powercondenser is disposed in adjacent, coextensive relationship on theupstream side of said refrigeration condenser.

4. In a heat pump system as set forth in claim 2 wherein saidrefrigeration system includes a compressor driven by said powercondenser.

5. In a heat pump system as set forth in claim 1 wherein said airflowducts include multi-speed means for directing the flow of air throughone of said ducts at a speed different than the flow of air through saidother duct.

1. In a heat pump system having parallel abutting airflow ductscommunicative with zones of different temperature, the improvementcomprising a heat exchange assembly including a compressor with drivingmeans therefore, and evaporator and at least one condenser, saidcondenser and evaporator of said heat assembly mounted on a rotatablemember in an opening between said ducts with said compressor and drivingmeans therefore arranged externally of said ducts, said condensermounted on said rotatable member on one side of the axis of rotation ofsaid member, said evaporator mounted in adjacent, substantially coplanarrelationship to said condenser on the other side of said axis ofrotation of said member, and a panel mounted substantially normal tosaid condenser and evaporator and intercepting said axis of rotation,said opening being substantially equal in area to the combined area ofsaid condenser and evaporator, said panel being coextensive andalignable in said opening with the common walls of said ducts to provideflow division there between.
 2. A heat pump system in accordance withclaim 1 wherein said heat pump comprises a vaporized fluid power systemincluding a power condenser, and a closed cycle refrigeration systemincluding a refrigeration condenser.
 3. A heat pump system in accordancewith claim 2 wherein said power condenser is disposed in adjacent,coextensive relationship on the upstream side of said refrigerationcondenser.
 4. In a heat pump system as set forth in claim 2 wherein saidrefrigeration system includes a compressor driven by said powercondenser.
 5. In a heat pump system as set forth in claim 1 wherein saidairflow ducts include multi-speed means for directing the flow of airthrough one of said ducts at a speed different than the flow of airthrough said other duct.